KR20170099775A - Double clutch with wear compensation, in particular for a motor vehicle - Google Patents

Abstract

The present invention relates to a double clutch (1) with compensation for wear, notably for a motor vehicle, comprising: at least one reaction plate (4); first and second friction disks (5a, 5b); first and second pressure plates (3a, 3b) individually operated by first and second diaphragms (9a, 9b); a fixing type cover (6); a first wear detection and compensation means installed between the first diaphragm (9a) and the fixing cover (6); and a second wear detection and compensation means installed between the second diaphragm (9b) and the second pressure plate (3b).

Description

[0001] The present invention relates to a double clutch for a vehicle,

The present invention particularly relates to a wear-compensating double clutch for an automobile.

The clutch device typically includes a reaction plate, a movable pressure plate, and a friction disk mounted between the reaction plate and the pressure plate. The movement of the pressure plate is controlled by a diaphragm, which is controlled by a clutch bearing.

Thus, the pressure plate moves between a clutch connecting position where the friction disc is clamped between the pressure plate and the reaction plate, and a clutch disengaging position where the friction disc is released.

The use of a clutch device causes wear of the lining of the friction disk and wear of the associated reaction plate and the corresponding material of the pressure plate. This is caused by a change in position of the pressure plate relative to the associated diaphragm and / or to the reaction plate, resulting in a change in the tightening load of the friction disk and a change in the course of the clutch bearing and the shifting point. The flying point is the position at which torque can begin to be transmitted through the clutch device.

A wear correction clutch device is known from document FR 2 780 119. A pressure plate designed to be supported on the friction disc, a pressure plate inserted between the pressure plate and the cover such that the pressure plate is fully clutch-coupled to the friction disc and a pressure plate A diaphragm is provided which serves to actuate the pressure plate between fully clutch disengaged positions, away from the friction disk, via the restoring means of the pressure plate.

The wear correction means of the friction disk includes a ramp cooperating with a counter-ramp inserted between the diaphragm and the pressure plate and comprising at least one compensating member moving in a predetermined range, And compensates for wear of the friction disk according to the angular position of the ramp relative to the counter-ramp.

The apparatus may further comprise wear detection means capable of displacing the movable compensation member when the friction disk is worn and capable of interfering with such displacement if the wear is insufficient, And a ramp cooperating with a counter-ramp that includes at least one detecting member moving in the range and located on the pressure plate side.

Finally, such an arrangement comprises at least a pressing member which constrains the lamps of the movable members relative to the associated counter ramp, and the pressing member may cooperate with the stationary stopper in such a manner as to release the movable members when wear of the friction disc is detected .

The movable compensating member is driven by a spring to correct the gap between itself and the pressing member when the movable compensating member is released by the pressing member and by the diaphragm. On the other hand, the movable detecting member is driven by another spring to correct the gap between itself and the pressing member when the movable detecting member is released by the pressing member and by the diaphragm.

In operation, the unit alternates between a continuous clutch engagement phase and a clutch release phase.

In the clutch connecting step, the diaphragm is supported on the pressure plate via the gap compensating member. In the clutch disengaging step, the pressure plate is restored toward its clutch disengaging position via restoring means which generally take the form of an elastically deformable tab.

When the friction disk is not worn and the corresponding material of the pressure plate and the reaction plate is not worn, the pressing member continuously keeps the detecting member and the compensating member supported on the pressure disk, so that these members are immobilized.

In the case of abrasion, the pressing member is supported on the stopper, and a gap is created between the pressing member and the detecting member. Since this detecting member is restricted by the spring, it is displaced in such a manner as to fill the gap. In the clutch connecting position, the load applied by the diaphragm on the compensating member hinders the displacement of the compensating member due to the support and friction on the pressure plate. Subsequently, when the diaphragm is displaced to its clutch disengaging position, the restoring tab of the pressure plate pushes the pressure plate against the gap compensating member and pushes the gap compensating member against the diaphragm. The load applied by the restitution tab is relatively small so that the displacement of the gap compensating member can be allowed even under the stress applied by the corresponding spring, despite the friction at the gap. This gap makes it possible to correct the gap between the pressing member and the correction member. Thus, wear of the friction plate and wear of the associated reaction plate and the corresponding material of the pressure plate are corrected.

This operation requires the use of a restoring means of the pressure plate which applies a relatively small load so as to enable displacement of the compensating member, in particular despite friction in the gap. This means of restoration is detrimental to operation since it can transmit axial vibrations to cause pumping of the pressure plate.

To solve this problem, the patent application FR 3 009 592 in the name of the present applicant discloses a pressure plate designed to be supported on a friction disk of a clutch device, a position where the pressure plate is fully clutch- And a diaphragm serving to actuate the pressure plate between fully clutch disengaged positions, away from the friction disc, via restoring means of the pressure plate. In the clutch device,

- means for correcting abrasion of the friction disc inserted between the diaphragm and the pressure plate, characterized in that it includes a ramp cooperating with a counter-ramp comprising at least one compensating member moving in a predetermined range and located on the pressure plate side, Which compensates wear of the friction disk according to the position of the ramp relative to the counter-ramp,

Wear detection means capable of displacing the movable compensation member in the case of abrasion of the friction disk and interfering with such displacement when the wear is insufficient, the wear detection means comprising at least one detection member movable in a predetermined range with respect to the movable compensation member And a lamp cooperating with a counter-lamp located on the pressure plate side,

At least one pushing member constraining at least the lamp of the detecting member relative to the associated counter-ramp, at least one pushing member capable of cooperating with the stationary stopper in such a manner as to release the movable members when wear of the friction disc is detected, And a wear correction mechanism,

The movable compensating member is driven to displace when the movable compensating member is released by the diaphragm,

- the movable detecting member is displaced when the movable detecting member is released by the pressing member and the diaphragm and is driven to at least partially correct the gap between itself and the pressing member.

The diaphragm also releases the movable compensating member and disrupts the displacement of the movable compensating member. In the fully clutch disengaged position, the diaphragm releases the movable compensating member and interferes with the displacement of the movable sensing member, Is always supported on at least one of the movable members between its fully clutch engaged position and fully clutch disengaged position.

In this way, the restoring means of the pressure plate can apply a large load, which is then taken over by the movable compensating member, followed by the diaphragm or the movable detecting member, and then by the diaphragm depending on the position of the diaphragm. In fact, since the movable members are not subjected to the load applied by the restoring means of the pressure plate at the time of their displacement, it is possible to easily cause these displacements in case of abrasion.

As described above, it is possible to restrict the transmission of the axial vibration and to prevent the pumping phenomenon of the pressure plate, since the restoring means of the pressure plate for applying a large load, such as, for example, .

The movable detecting member and the movable compensating member are driven by an elastic member such as a tension spring.

In particular, at least one first tension spring extending in the circumferential direction is installed between the detecting member and the pressure plate or between the cover and the detecting member rotatably coupled to the pressure plate. A second tension spring extending in the circumferential direction is provided between the detecting member and the compensating member. These second springs ensure the motorization function of the compensating member with respect to the detecting member.

The patent application FR 3 009 592 also applies such abrasion correction means to the dual clutches.

The dual clutch can be alternately connected to the two coaxial input shafts of the gearbox, which can be a motorized engine shaft in particular.

Thus, the dual clutch can change the gear ratio while maintaining the transmission of the engine torque to the vehicle's wheels. In practice, two clutches are associated with the even and odd gear ratios, respectively. When the gear ratio is changed, the first clutch is disengaged and the second clutch is engaged, so that the engine torque is gradually transferred from the first clutch to the second clutch.

Each clutch includes a lid and a mechanism including a diaphragm designed to cooperate with a pressure plate driven by rotation of the engine shaft. Each diaphragm can be displaced by a corresponding clutch bearing between a rest position and an active position. Depending on the type of clutch, the active position of the diaphragm corresponds to the connection or disconnection of the gearbox and the engine shaft and the rest position of the diaphragm corresponds to the disconnection or connection of these shafts. Thus, they are called normal open clutches and normal closed clutches, respectively.

For safety reasons, at least one of the clutches is normally open type.

The clutch bearing is controlled by an actuator controlled by an electronic calculator to apply a predetermined force to the diaphragm to displace it by a predetermined distance.

The pressure plate of each clutch driven by the corresponding diaphragm is designed to clamp the friction disc on the corresponding reaction plate. One reaction plate may be provided for each clutch. In a variant, a unique reaction plate is used which is common to the two clutches provided between the two friction discs.

Each friction disc is rotationally connected to the input shaft of the gearbox and each reaction plate rotates in unison with, for example, a flywheel connected to the engine shaft. This allows the friction disc to be tightened between the corresponding reaction plate and the pressure plate so that torque can be transmitted between the shaft of the associated gearbox and the engine shaft.

As described above, the use of the clutch causes wear of the friction lining of the friction disk and wear of the associated reaction plate and the corresponding material of the pressure plate. This is caused by a change in the position of each pressure plate relative to the associated diaphragm and / or to the reaction plate, resulting in changes in the thrust load of the friction disc and in the course of the clutch bearing and in the shifting of the biting point. In this case, the balancing point is the position at which the engine torque begins to be transmitted to the shaft of the gearbox when the clutch is closed.

In general, this wear is more pronounced on the first clutch, i.e. on the reaction plate and the pressure plate and on the friction discs belonging to the clutch associated with the odd gear ratio. Thus, when the dual clutch includes only a single wear correction mechanism according to the present invention, it preferably forms part of the first clutch. Of course, the dual clutch according to the present invention can simultaneously include the wear correction mechanism mounted on the first clutch and the mechanism mounted on the second clutch.

The patent application FR 3 009 592 discloses the use of a first wear compensation mechanism, particularly mounted on the first clutch, and a second wear compensation mechanism, mounted on the second clutch.

The compensation member of the first wear compensation mechanism includes a leg that engages in the notch of the corresponding detection member such that the angular displacement of the compensation member relative to the detection member is limited.

On the other hand, a first tension spring is provided between the detecting member and the movable cover, and a second tension spring is installed between the detecting member and the compensating member, in the respective zones of the notch corresponding to the bearing legs.

The present invention proposes a simple, efficient, and inexpensive alternative to such a structure.

To this end,

At least one reaction plate, centered on the rotation axis, designed to be rotationally coupled to the drive shaft,

- first and second friction discs, each having a friction lining, designed to be coupled to first and second driven shafts, respectively,

First and second pressure plates respectively actuated by the first and second diaphragms in such a manner as to tighten or loosen the first and second friction discs on the reaction plate, First and second pressure plates fixedly connected to the moving lid and actuated by supporting the first diaphragm on the movable lid,

A stationary lid secured to the reaction plate and containing a second pressure plate, a second friction disc and / or a second diaphragm,

A wear-compensating dual clutch, in particular for motor vehicles, comprising first wear detection and correction means capable of correcting wear of a first friction disk,

The first wear detection and correction means,

A first abrasion correction means inserted between a first diaphragm and a fixed lid, comprising: a ramp cooperating with a counter-ramp including at least one compensating member moving in a predetermined range and located on the fixed lid side, A first wear compensation means for adjusting the distance between the fixed cover and the fixed cover and compensating for the corresponding wear according to the position of the ramp relative to the counter-

A first abrasion detecting means capable of displacing a movable compensating member in the case of abrasion and capable of interfering with such displacement when such abrasion is insufficient, comprising at least one movable detecting member in a predetermined range with respect to the movable compensating member, And a lamp cooperating with a counter-ramp located on the side of the first lamp,

At least one first urging member constraining at least a ramp of a detecting member relative to an associated counter-ramp, at least one first urging member capable of cooperating with a stationary stopper releasing the detecting member when abrasion is detected, Lt; / RTI >

The movable compensating member is driven to be displaced when the movable compensating member is released by the first diaphragm,

The movable detecting member is provided with a biasing member which is displaced when the movable detecting member is released by the pressing member and by the first diaphragm, As a result,

The detecting member includes at least one leg that can be supported on the corresponding at least one bearing of the movable compensating member so that the displacement of the detecting member relative to the movable compensating member is limited, Is fixed to or engaged with the leg of the detecting member.

Thus, the legs of the detecting member simultaneously ensure a bearing function to limit the relative clearance of the detecting member relative to the mobile compensating member by avoiding all overcompensation of wear of the first friction disk, and a function of locking or unlocking the elastic member .

The dual clutch may also include a second wear detection and correction means capable of correcting wear of the second friction disk,

A second abrasion correction means inserted between the second diaphragm and the second pressure plate, the second abrasion correction means including a ramp cooperating with a counter-ramp including at least one compensating member moving in a predetermined range and located on the second pressure plate side, A second abrasion correction means for adjusting the distance between the second diaphragm and the second pressure plate and compensating for the corresponding abrasion according to the position of the ramp relative to the counter-

A second abrasion detecting means capable of displacing the movable compensating member in the case of abrasion and capable of interfering with such displacement when such abrasion is insufficient is characterized by comprising at least one movable detecting member in a predetermined range with respect to the movable compensating member, A second abrasion detection means including a ramp cooperating with a counter-ramp located on the pressure plate side,

At least one second biasing member constraining at least the lamp of the detecting member relative to the associated counter-ramp, at least one second biasing member capable of cooperating with the stationary stopper in such a manner as to release the corresponding detecting member when wear is detected, And a pressing member,

The movable compensation member is driven to be displaced when the movable compensation member is released by the second diaphragm,

The movable detecting member is driven by the elastic member to be displaced when the movable detecting member is released by the second pressing member and by the second diaphragm so as to at least partially correct the gap between itself and the pressing member,

The detecting member includes at least one leg that can be supported on the corresponding at least one bearing of the movable compensating member so that the displacement of the detecting member relative to the movable compensating member is limited, Or fixed to the legs of the detecting member.

As described above, the legs of the detecting member of the second wear detection and correction means thus have a bearing function to limit the relative clearance of the detecting member relative to the mobile compensating member by avoiding any overcompensation of wear of the second friction disc, and , And the function of fixing or hanging the elastic member is ensured at the same time.

The legs of the detecting member of the first or second wear detection and correction means traverse the notch of the corresponding compensating member and the legs can be bearing supported against the edge of the notch.

Thus, the width of the notch, i.e. the distance between the side edges of the notch on the one hand and the width of the leg on the other hand, defines the possible clearance between the detecting member and the compensating member.

The notch may be open towards the stationary lid or the second pressure plate side. In this way, the abrasion correction means is compact in the axial direction.

The legs can be inserted axially between the fixed cover or the counter ramp of the second pressure plate and the movable compensation member.

The compensating member is supported and held against the stationary cover or the second pressure plate, in particular during operation, so that the corresponding legs are prevented from falling out of the notch, for example under a vibration effect. On the other hand, such a notch does not disturb the support of the diaphragm relative to the compensation member which is opposed to the notch. This ensures a uniform support of the diaphragm with respect to the compensating member.

The notch may be disposed at an angle between two consecutive lamps of the movable compensation member.

The detecting member can pivot with respect to the wear compensating member about the axis and the legs of the detecting member limit the moving angular distance of the detecting member relative to the wear compensating member to an angle of less than 5 DEG.

Such a travel distance is sufficient to ensure the operation of the wear detection and correction means while preventing excessive compensation of wear of the friction disk.

The elastic member for driving the detection member of the first or second wear detection and correction means may include an end formed by the wire in the form of a hook engaging in a notch or groove in the leg of the corresponding detection member.

Therefore, the hooking operation in the installation of the double clutch can be realized simply and quickly. Of course, the dimension of the notch or groove is adjusted to the diameter of the wire of the elastic member.

The movable compensation member and the detection member of the first or second wear detection and correction means may each include an annular portion including a corresponding ramp, wherein the annular portion of the detection member is located radially outward of the annular portion of the compensation member, The free end of the leg is located radially inward of the annular portion of the compensating member and the elastic member driving the corresponding detecting member is fixed to the free end of the leg .

The pressure plate, the reaction plate, the friction disk, the diaphragm, the detecting member, the wear compensation member, the fixed cover and / or the movable cover may be annular and substantially co-axial.

The dual clutch includes a centering member fixed to or fixed to the stationary cover and the centering member includes a cylindrical guide surface or is partially cylindrical and the detecting member of the first wear detection and correction means is annular, The centering of the detecting member is ensured by including three or more legs extending in the direction of the centering member and supported on the centering surface of the centering member.

Therefore, good positioning of the detecting member with respect to the first diaphragm is secured, and this diaphragm applies a load that is accurately distributed on the detecting member.

The elastic member for driving the detection member of the first detection wear correction means can be supported in the radial direction on the centering surface located radially outwardly of the elastic member.

Therefore, the centering surface can also keep the elastic member in an operating state when the elastic member receives a large centrifugal force. The centering member can thus simultaneously realize the centering function of the detecting member and the supporting function of the elastic member. Thus, the cost and complexity of the dual clutch are reduced.

The centering member may include at least one flange or leg that extends in the axial direction and is located radially inward of the elastic member, and the elastic member may be supported radially inwardly on the flange or leg in the radial direction.

In the case where the elastic member is, for example, a linear spring, it is intended to regain its linear shape when it is not subjected to a large centrifugal force. In this case, for example, it is necessary to limit the deformation of the spring in order to keep the spring in a bent posture. Thus, the resilient member is held in the annular space defined between the radially outward centering surface and the radially inwardly described flange or leg. Such a flange or leg may be replaced by, for example, a cylindrical surface that is positioned radially inward of the elastic member and ensures the same function.

The elastic member for driving the detection member of the first wear detection and correction means may include an end fixed to the centering member and an end fixed to one of the centering legs of the detection member.

Therefore, the centering member also ensures the function of hanging the elastic member.

The centering member may comprise a leg or projecting zone extending radially outwardly, preferably three or more legs or projecting zones, and the mobile compensating member of the first wear detection and correction means may be supported So as to realize the centering of the correction member.

The centering member can thus simultaneously ensure the centering of the corresponding detecting member and the corresponding centering of the compensating member.

The legs or projections may have a rounded radially inner end designed to form a pointed or nearly pointed support on a corresponding compensating member. Therefore, the quality of the centering realized is improved.

The double clutch includes a bearing member connected to the second pressing member, the bearing member being designed to separate the second pressing member from the corresponding detecting member and / or the compensating member in the case of abrasion, A first end connected to the member, and a second end that can be axially supported with respect to a reference surface formed on the centering member.

As a result, the centering member simultaneously ensures the centering function of the detecting member and the axial reference function for the bearing member.

The centering member and the stationary lid may each include at least one aperture for passing a bearing member, the aperture of the centering member being surrounded by a flange, the flange extending in the axial direction and the free end forming a reference plane , The second end of the bearing member includes an enlarged head which can be supported on the free end of the flange of the centering member.

The first diaphragm may include an annular portion from which the fingers extend radially inwardly and the centering member may comprise an axially extending leg, preferably three or more, extending between the fingers of the first diaphragm Legs.

Whereby the legs of the centering member can ensure centering of the first diaphragm. The centering of the first diaphragm assures good positioning of the diaphragm relative to the clutch bearing, thereby improving the operation of the dual clutch.

The dual clutch according to the present invention may also include one or more of the following features:

- The centering element is welded to the lid or made integral with the lid.

The end of each centering leg has an axially extending portion in which a rounded corrugation or protruding region is formed to form a pointed or nearly pointed support on the centering surface.

- The centering elements are fixed by rivets on a fixed cover.

The centering member comprises an annular flat portion extending in the radial direction and supported on the fixed lid, the centering member further comprising a cylindrical flange defining a centering surface, the flange extending axially from the annular flat portion.

The bearing member is connected to the second pressing member in the region located between the corresponding detecting member and the compensating member, preferably between the detecting member and the compensating member. As a result, the vibration effect of the pressing member, which affects the position of the actual supporting region of the detecting member and / or the pressing member on the correcting member, is limited. Thus, the above-described features can control the position of the movable members to ensure good operation of the corresponding wear detection and correction means.

The first diaphragm or the second diaphragm releases the corresponding movable detection member at the fully clutch engaged position and interferes with the displacement of the corresponding movable compensation member, and the first diaphragm or the second diaphragm, at the fully clutch disengaged position, The first diaphragm or the second diaphragm is always supported on at least one of the movable members between a fully clutch engaged position and a fully clutch disengaged position.

Each movable detection member is in the form of a ring and the ring has an end which can serve to support the corresponding diaphragm and a circumferentially extending portion cooperating with an associated counter ramp of the second pressure plate or fixed cover side The lamp comprising at least one lamp.

Each movable compensating member is in the form of a ring and the ring has an end capable of supporting the corresponding diaphragm and a circumferential direction cooperating with an associated counter ramp located on the second pressure plate or fixed cover side RTI ID = 0.0 > lamp < / RTI >

The movable compensating member and the movable detecting member are concentric.

The pressing member includes at least one elastic tab, and one end of the elastic tab can be supported on the corresponding movable detecting member or the movable compensating member.

The bearing member is connected to each of the pressing members and the bearing member is designed to separate the pressing member from the detecting member and / or the correcting member in case of abrasion, and the bearing member, in the region located between the detecting member and the correcting member, And is preferably connected to the pressing member in the middle between the detecting member and the compensating member.

The first pressure plate is restored to its clutch disengaging position against the reaction plate by first elastic restoring means, for example, a first elastic restoring tab provided between the first pressure plate and the reaction plate.

The second pressure plate is restored to its clutch disengaging position against the reaction plate by means of second elastic restoring means such as a second resilient restoring tab provided between the second pressure plate and the reaction plate.

- Elastic taps ensure rotational coupling of reaction plate and pressure plates.

The first clutch is normally open type.

- The second clutch is normally open type.

The dual clutch includes a first friction disc and a unique reaction plate serving to support the second friction disc.

The dual clutch comprises a movable cover fixedly connected to the first pressure plate and actuated by the oscillation of the first diaphragm.

The first diaphragm is in the form of an elastic annular metal sheet and is installed in a vibratory fashion about the support area of the movable cover.

The second diaphragm is in the form of a resilient annular metal sheet and its radially outer portion is mounted in an oscillating manner with respect to the stationary lid.

The elastic member keeps the radially outer portion of the second diaphragm supported on the stationary lid.

The fixed cover comprises a radial clamp which serves to fix on the reaction plate, which is connected to the annular portion at least partially surrounding the second pressure plate, the second friction disc and / or the second diaphragm, The annular portion is extended by an annular portion extending radially inwards.

- A counter-ramp is provided in the radial part of the fixed cover.

The mobile lid includes a radially outer portion extending from the first pressure plate and partially surrounding the stationary lid, extending by a portion extending radially inwardly and serving to support the first diaphragm.

- the angles of the lamps of the movable members and the associated counter-lamp are comprised between 2 and 20 degrees.

The detecting member is located radially outward of the corresponding wear-compensating member.

A first elastic member, for example a circumferentially extending tension spring, is installed on the one hand between the corresponding detecting member and the fixed cover or the second pressure plate on the other hand.

A second elastic member such as a pin-like spring, for example, is provided between each of the detecting members and the corresponding compensating member.

The first elastic member applies a tangential or circumferential load greater than the tangential or circumferential load applied by the second elastic member.

The length of the first elastic member is large enough to cause displacement of the detecting member in a large angular range of, for example, about 120 degrees.

Each pressure element is in the form of an elastic tab which applies an axial load.

The pressing member is fixed to the fixed cover at the first end and is fixed on the corresponding wear detection member and the correction member at the second end, for example on the first movable detection and correction member, And on the compensating member, thereby constraining the lamp to be supported on the counter-ramp.

The pressing member may be fixed to the pressure plate at the first end and supported on the corresponding abrasion detecting member and the compensating member at the second end, for example on the second movable detecting and compensating member, - constrained to be supported on the ramp.

The bearing element is fixed to the second end of the elastic tab.

The bearing element is arranged between the corresponding wear detecting element and the compensating element in the radial direction, preferably in the radial direction, between the movable elements, for example by a first end fixed by riveting, And a cylindrical second end that defines an enlarged head of larger dimension and defines a shoulder.

The enlarged head of the bearing stud can be supported on the radial surface of the movable cover, the fixed cover or the centering element.

The enlarged head of the bearing stud is designed to be supported on the corresponding radial surface when the displacement of the corresponding pressure plate is large, i.e. the lining of the friction disk and / or the wear of the associated material of the associated reaction plate and pressure plate is large .

The detecting member and the compensating member comprise at least one zone in which they are spaced apart from one another in the radial direction.

The detecting member and the compensating member are in the form of a generally circular shape having at least one region provided with convex portions locally spaced apart from each other in the radial direction as viewed from the front, Lt; / RTI >

The pressing member exerts an urging force to be distributed between the detecting member and the compensating member and the axial component of this force along the axis X can be applied on the application radius located between the detecting member and the compensating member.

The movable compensating member and the movable detecting member are concentric.

The detecting member and the compensating member in the form of a circle generally include at least one region provided with convex portions in which the movable members are locally spaced apart from each other in the radial direction and the pressing member is arranged in the region where the convex portions are provided, Lt; / RTI >

The end of the bearing member connected to the pressing member is accommodated in the region provided with the convex portion.

BRIEF DESCRIPTION OF THE DRAWINGS The invention will be better understood by reference to the following detailed description, taken in conjunction with the accompanying drawings, as non-limiting embodiments, and other details, features and advantages of the invention will become apparent:
1 is an exploded perspective view of a dual clutch,
2 is an axial sectional view of the dual clutch,
3 is an axial half sectional view of a portion of the dual clutch,
Figure 4 is a partially broken perspective view of a dual clutch,
5 is a perspective view of a portion of the dual clutch,
6, 7 and 8 are detailed perspective views of the dual clutch,
9 is a detailed view showing a wear detection member and a correction member mounted on the first clutch,
10 is an axial cross-sectional detail view of a portion of the dual clutch,
11 is a perspective view of the centering member,
12 is a front view showing a part of the first wear detection and correction means and the centering member,
13 is a perspective view showing a part of the second wear detection and correction means and the second pressure plate,
14 is a detailed perspective view of a portion of the second wear detection and correction means and the second pressure plate,
15 is a detailed cross-sectional view of a portion of the second wear detection and correction means and the second pressure plate,
Figs. 16 to 19 are schematic views showing the operation of the first clutch when there is no wear,
20 to 27 are schematic views showing the operation of the first clutch in case of wear,
28 to 31 are schematic views showing the operation of the second clutch in the absence of wear,
32 to 39 are schematic views showing the operation of the second clutch in case of wear;

In the drawings, there is shown a wear compensating dual clutch 1 according to an embodiment of the present invention. It is designed to couple the engine with the first and second input shafts (not shown) of the gearbox. The axis of the dual clutch is indicated by X. The dual clutch 1 includes first and second clutches 2a and 2b (also referred to as clutch mechanisms) having different gear shifts.

The first clutch 2a includes a first pressure plate 3a and a reaction plate 4, and a first friction disk 5a extends therebetween. The first pressure plate 3a is rotatably coupled to the reaction plate 4 and has a clutch connecting position for tightening the first friction disc 5a on the reaction plate 4 or releasing the first friction disc 5a, And moves translationally relative to the reaction plate between the discrete locations.

The reaction plate 4 is fixed on a lid 6 called a fixed lid, and the lid itself is designed to be coupled to the engine shaft. The first friction disk 5a is designed to be coupled to the first input shaft of the gearbox. Thus, at the clutch connecting position of the first clutch 2a, the engine shaft is coupled to the first input shaft of the gearbox.

The first pressure plate 3a extends forward and is fixed on the movable lid 7 in translational motion with respect to the reaction plate 4 and the fixed lid 6. A first elastic restoring tab 8a is provided between the first pressure plate 3a and the reaction plate 4. [

The first clutch 2a further includes a first diaphragm 9a existing in the form of an elastic annular metal sheet and is installed to vibrate around the support portion 10 of the movable lid 7. [

Control of the first clutch 2a is typically accomplished by a first clutch bearing (not shown) cooperating with the radially inner periphery of the first diaphragm 9a. The first diaphragm 9a forms a lever that transmits a force applied by the first clutch bearing to the first pressure plate 3a via the movable lid 7.

In order to effectively tighten the first friction disc 3a, the first diaphragm 9a is preloaded in a rest state. Without such an example load, the first diaphragm 9a is in an elastic state requiring a course initiation of a relatively large first clutch bearing in order to apply an efficient thrust load to the first friction disc 3a in a rest state do. When the first clutch bearing is actuated, it is in equilibrium with the preload of the first diaphragm 9a before starting to tighten the first friction disk 3a. It is possible to reduce the course of approach of the first clutch bearing to tighten the first friction disk 3a, which is preliminarily set in the first diaphragm 9a, for example, on the ball bearing of the first clutch bearing and on the double clutch 1 So that it can always have a minimum preload load on the ball bearing supporting it. Therefore, the life of the bearing is increased and the vibration of the double clutch 1 is limited.

The first clutch 2a is normally open type. Thus, the rest position of the first diaphragm 9a corresponds to the clutch disengagement state of the first clutch 2a. The first diaphragm 9a preferably has a portion of a disc spring washer-type that is capable of restoring the first diaphragm 9a toward its rest position.

When the first diaphragm 9a is in the rest position, i.e. when the first bearing does not apply any load to the first diaphragm 9a, the first diaphragm 9a exerts a load on the first pressure plate 3a (Or almost) not. The first pressure plate 3a is released from the reaction plate 4 via the elastic tab 8a to release the first friction disk 5a.

The second clutch 2b includes a second pressure plate 3b and a second friction disc 5b extending radially between the reaction plate 4 and the second pressure plate 3b. Thereby, the same reaction plate 4 is used for the two clutches 2a and 2b, and each of the friction discs 5a and 5b is disposed on one side of the two radial bearing surfaces of the reaction plate 4. [ And a second elastic restoring tab 8b is provided between the second pressure plate 3b and the reaction plate 4. [

The second pressure plate 3b is rotatably coupled to the reaction plate 4 and has a clutch connection position for tightening the second friction disc 5b on the reaction plate 4 or releasing the second friction disc 5b, And moves translationally relative to the reaction plate between the discrete locations.

The second friction disc 5b is coupled to the second input shaft of the gearbox. Thereby, at the clutch connecting position of the second clutch 2b, the engine shaft is coupled to the second input shaft of the gearbox.

The second clutch 2b further includes a second diaphragm 9b present in the form of a resilient annular metal sheet, the radially outer portion of which is mounted in an oscillating manner with respect to the stationary lid. An elastic member or washer 11 holds the radially outer portion 12 of the second diaphragm in the support 12 on the fixed lid 6 (Fig. 4). The support 12 may be embodied by a metal ring or an annular surface. In a variant, this support is embodied by a protrusion directly from the stationary lid 6.

The control of the second clutch 2b is typically performed by a second clutch bearing (not shown) cooperating with the radially inner periphery of the second diaphragm 9b via a load transmission device (not shown) . The second diaphragm 9b forms a lever that transmits a force applied by the second clutch bearing 20 to the second pressure plate 3b so that the second friction disk 5b can be efficiently tightened.

The second clutch 2b is also normally open type. When the second diaphragm 9b is in the rest position, i.e. when the second clutch bearing does not apply any load to the second diaphragm 9b at all, the second diaphragm 9b is placed on the second pressure plate 3b No (or almost) no load is applied. The second pressure plate 3b is released from the reaction plate 4 via the elastic tab 8b to release the second friction disc 3b.

The fixed cover 6 is connected to the annular portion 6b at least partially surrounding the second pressure plate 3b, the second friction disk 5b and / or the second diaphragm 9b from the rear to the front And a radial clamp 6a, which serves to fix the reaction plate 4 to the base plate. The annular portion 6b is extended by an annular portion 6c extending radially inwards.

On the other hand, the movable lid 7 is provided with a first pressure plate 3a extending forward radially inwardly and forwardly by a portion 7b which contributes to the support 10 of the first diaphragm 9a, And a radially outer side portion 7a which partially extends around the fixed lid 6. [

To compensate for wear of the first friction disc 5a, the first pressure plate 3a and / or the reaction plate 4, the first clutch 2a is equipped with a first wear detection and correction means.

The first wear detection and correction means mounted on the first clutch 2a is provided between the stationary lid 6 and the first diaphragm 9a in the axial direction and more precisely between the first diaphragm 9a and the fixed lid 9a in the axial direction, Is inserted between the radial portions (6c) of the base (6).

The first abrasion detection and correction means includes a first movable compensating member (13a) present in the form of a ring, the first movable compensating member having an end capable of supporting the first diaphragm (9a) Has an end including at least one lamp 14a extending in the circumferential direction in cooperation with an associated counter-lamp 15a provided in the radial portion 6c of the lid 6 (see, e.g., Fig. 6). Of course, the counter-ramp 15a can be formed by an independent member and fixed to the stationary lid 6.

The first wear detection and correction means also includes a first movable detection member 16a present in the form of a ring, the first movable detection member having an end capable of supporting the first diaphragm 9a, (See, e.g., Fig. 6), which includes at least one lamp 17a extending in the circumferential direction in cooperation with the counter-ramp 15a of the radial portion 6c of the housing 6.

For example, the angles of the lamps 14a, 17a of the movable members 13a, 16a and the counter-ramp 15a of the fixed lid 6 are comprised between 2 and 20 degrees.

The two movable members 13a and 16a are concentric and separated from each other, and the first detecting member 16a is located radially outside the first wear-compensating member 13a. In a variant, the position of each of the movable members 13a, 16a can be reversed. However, the possibility of reversal of the movable members 13a, 16a is associated with the internal architecture of the mechanism.

8 to 10, the detecting member 16a is a member which extends inward in the radial direction by crossing the notch 27a formed in the wear-compensating member 13a in the radial direction, for example, Three centering legs 26a. Each centering leg 26a includes a U-shaped or hooked shape at its free end, wherein a rounded corrugation 28 or a projecting area is provided. The notch 27a is disposed at an angle between two consecutive lamps of the movable compensating member 13a.

The leg 26a is inserted between the movable compensating member 13a and the counter ramp 15a of the fixed lid 6 along the X axis.

The centering means ensures good positioning of the movable members 13a, 16a.

In particular, the centering means comprises an annular centering member 29 as best seen in Fig. 11, which includes a planar section 29a extending in the radial direction and supported in the radial section 6c of the stationary lid 6, ). The planar section 29a is provided at its radially inner periphery with a first leg 22 which extends through the radial inward direction and which passes through a rivet 30 which can secure the centering member 29 to the fixed lid 6. [ Or a lobe 29b.

The planar section 29a is provided at its radially inner periphery with a second leg or lobe 29 that includes apertures that extend radially inwardly and serve to secure a pin 31 that can center the second diaphragm 9b (Fig. 1, Fig. 2 and Fig. 11). In particular, the centering pin 31 extends between the fingers of the second diaphragm 9b.

The planar section 29a further comprises a third leg or lobe 29d in its radially inner perimeter (Figs. 8 and 11), which third leg or lobe extends radially inward and forms a flange or cylindrical connection the flange or the cylindrical communication extending in the axial direction and the free end of which forms a radial reference surface 29f whose position is known and which is fixed with respect to the fixed lid 6, do.

The legs 29g are retracted from the radially inner periphery of the annular planar section 29a and extend axially opposite the fixed lid 6.

A cylindrical flange 29h extends axially from the radially outer portion of the annular planar region. The radially inner surface 29i of the cylindrical flange 29h forms a guide surface. The centering legs 26 of the detecting member 16a and in particular the rounded corrugations 28 of the legs 26 can be supported on the centering face 29i described above and the centering legs 26 of the detecting member 16a Ensure centering.

The flange 29h is also capable of hanging the end portion of each elastic member 18a.

For example, three legs 29j (Figs. 7 and 11) extend radially outwardly from the radial outer periphery of the planar section 29a of the centering member 29. As shown in Fig. The free end of the leg 29j is bent or rounded and supported on the inner surface of the compensating member 13a to realize its centering with respect to the fixed lid 6.

On the other hand, for example three legs 29k extend axially beyond the cylindrical flange 29h from the radially outer periphery of the planar section 29a. These legs 29k engage between the fingers of the first diaphragm 9a and realize its centering with respect to the fixed lid 6.

According to a modified example not shown, the centering member 29 is welded to the fixed lid 6 or made integral with the fixed lid.

For example, a first elastic member 18a such as a linear or curved tension spring is provided between the first detecting member 16a and the fixed lid 6.

More specifically, the first elastic member 18a has a hook-shaped end portion 18'a hooked to the centering member 29 and a hook-shaped end portion 18'a hooked to the centering leg 26a of the detection member 16a. And is formed of a wire.

Each end 18'a is formed in a flange 29h and engaged in a circumferentially open notch 29l (Fig. 11). On the other hand, each end 18 "a engages in a notch 26'a (Figs. 8 and 9) of the corresponding leg 26a.

When the elastic member 18a is subjected to the centrifugal force, the elastic member 18a can be supported on the centering face 29i of the radially outward cylindrical flange 29h. The elastic member 18a can also be supported on the legs 29g when it is desired to regain a linear shape. In other words, the elastic member 18a is held in the radial direction in the annular space formed between the cylindrical flange 29h and the leg 29g.

For example, a second elastic member 19a such as a pin spring is provided between the first detecting member 16a and the first compensating member 13a.

The length of each first spring 18a is large enough to cause displacement of the first detecting member 16a in a large angular range (e.g., about 120 deg.).

The first clutch 2a also includes at least one first urging member 20a (Figs. 1 and 2) present in the form of elastic taps that apply an axial load. The tab 20a may be secured to the fixed cover 6 in the first region and supported on the first detecting member 16a and substantially on the first wear compensating member 13a at the second end, To be supported on the radial portion 6c of the lid 6.

The bearing stud 21a is fixed on the second section of the tab 20a. The bearing stud 21a is arranged in the radial direction between the first detecting member 16a and the first wear compensating member 13a and preferably in the radial direction between the movable members 13a and 16a, A second end 23a (Figs. 2 and 4) that defines an enlarged head of larger dimensions than the rest of the stud 21a and defines a shoulder, . The stud 21a may be supported on a radial bottom surface formed by a countersink 24 across the opening of the mobile lid 7 and provided on the mobile lid 7. [

In particular, the enlarged head 23a of the bearing stud 21a is located at a position where the displacement of the first pressure plate 3a is large, i.e., when the lining of the first friction disk 5a and / Is designed to be supported on the bottom surface of the counter sink (24) when the wear of the corresponding material of the pressure plate (3a) is large.

In order to be able to fix the first end 22a of the stud 21a on the tab 20a between the movable members 13a and 16a in the radial direction, As well as at least one zone 25 in which they are spaced apart from one another. As a result, the movable members 13a, 16a are arranged in a generally circular shape with at least one zone 25 provided with convex portions locally spaced from each other in the radial direction, And a second section of the tab 20a is supported on corresponding second ends of the movable members 13a, 16a in one of these sections 25.

Now, the operation of the first wear detection and correction means will be described with reference to Figs. 16 to 27. Fig. In these drawings, the centering member 29 is not shown.

As shown schematically in Figures 16-19, the first wear detection and correction means are arranged so that when the lining of the first friction disk 5a is not at all or substantially abraded and when the first pressure plate 3a and the linkage If the corresponding material of the reaction plate 4 is not worn, for example, if the accumulated axial wear is less than 0.05 mm, it will not work.

16, the first diaphragm 9a is supported on the first compensating member 13a at the completely clutch-connected position and in the absence of wear, so that the first pressure against the elastic restoring tab 8a, Push the plate 3a again. The first pressure plate 3a and the corresponding reaction plate 4 (fixed in the axial direction) thus tighten the first friction disc 5a with the lining. In this position, the head 23a of the bearing stud 21a reaches the same height as the bottom surface of the countersunk 24 of the movable lid 7.

Also in this position, the leg 26a is supported on the first edge 32a of the notch 27a of the compensating member 13a as shown in Fig.

On the other hand, as shown in Fig. 18, the first diaphragm 9a is supported on the first detecting member 16a, and the first diaphragm 9a and the first diaphragm 9b A gap is generated between corresponding ends of the compensating member 13a.

The leg 26a is in a state of being supported on the first edge 32a of the notch 27a of the compensating member 13a as shown in Fig.

Thus, in the absence of significant wear, the second region of the elastic tab 20a and / or the first diaphragm 9a can be moved in any direction, regardless of the actuation phase of the first clutch 2a (clutch engagement / disengagement of the clutch) It is confirmed that the detecting member 16a and the first compensating member 13a are supported and held on the fixed lid 6. [ In this case, the resistance torque generated by the friction between the members 13a, 16a and the fixed lid 6 is larger than the torque exerted by the springs 18a, 19a. Thus, the members 13a, 16a are immobilized in rotation with respect to the fixed lid 6, whatever the operating phase of the first clutch 2a.

20 to 27 show a state in which the lining of the first friction disc 5a (or the corresponding material of the first pressure plate 3a and the reaction plate 4) is significantly worn out to prevent malfunction of the first clutch 2a In the case where correction is required.

20, the head 23a of the bearing stud 21a is supported on the bottom surface of the countersunk 24 of the movable lid 7 at the fully clutch-connected position, so that the elastic tab 20a Is detached from the corresponding second end of the first detecting member 16a. Thus, a clearance j1 is formed between the second end of the first detecting member 16a and the second region of the tab 20a.

Therefore, even if the first pressing member 20a is supported on the corresponding second end of the first detecting member 16a, even if the first pressing member 20a and the corresponding second abutting member 13a of the first abrasion- There may be an axial gap between the ends.

In some cases, the end of the first detecting member 16a and the second end of the first detecting member 16a may be mixed. Likewise, the end of the first compensating member 13a and the second end of the first compensating member 13a can be mixed.

Accordingly, the first detecting member 16a, which is no longer subjected to the axial load, is rotationally interlocked by the first elastic member 18a to at least partially fill the gap j1 (Fig. 22). During this rotation, the second elastic member 19a is restricted. The rotational direction of the detecting member 16a with respect to the compensating member 13a is shown by an arrow R1 in Fig.

The rotation of the first detecting member 16a is stopped when the corresponding second end of the first detecting member 16a is again supported on the second section of the tab 20a, When the leg 26a is supported on the edge 33a (opposite the edge 32a) of the notch 27a of the compensating member 13a.

During this step, the first compensating member 13a is supported and held on the fixed lid 6 by the first diaphragm 9a. Thus, the member is immobilized in rotation with respect to the stationary lid 6. [

During the subsequent clutch separating step, the first diaphragm 9a transfers its support from the first compensating member 13a to the first detecting member 16a. Figs. 24-27 illustrate the location of these elements during this migration. During this clutch disengagement, the first pressure plate 3a releases the first friction disk 5a away from the reaction plate 4 via the corresponding restoring tab 8a.

As shown in Figs. 24 and 25, when the first diaphragm 9a is in the fully clutch disengaged position, the first correction member 13a is completely released. In this position, the first detecting member 16a is held on the first diaphragm 9a and on the fixed lid 6 so that the rotation is held fixed. On the other hand, the head 23a of the bearing stud 21a is separated from the bottom surface of the countersink 24 of the movable lid 7 and the second section of the movable tab 20a is connected to the corresponding part (J2) with respect to the two end portions.

Therefore, the first compensating member 13a, which is constrained by the second elastic member 19a, is rotationally interlocked as shown in Figs. 26 and 27 so that the distance between the first compensating member 13a and the tab 20a Thereby filling all or a part of the gap j2. The rotational direction of the compensating member 13a with respect to the detecting member 16a is shown by an arrow R2 in Fig.

The rotation of the first compensating member 13a can be achieved, for example, when the corresponding second end of the first compensating member 13a is again supported on the second section of the tab 20a, When the leg 26a is supported on the edge 32a of the notch 27a of the compensating member 13a, it is stopped.

The pivoting of the first compensating member 13a and the first detecting member 16a with respect to the fixed cover 6 is carried out by means of the lamps 14a and 17a and the counter- The axial distance between the support area of the first diaphragm 9a on the first friction disk 5a and the fixed lid 6 can be increased and thus the wear of the lining of the first friction disk 5a and / And the wear of the corresponding material of the reaction plate 4 can be gradually compensated.

This structure also allows the operating angle of the first diaphragm 9a to be maintained, so that a constant preload load is maintained and the mechanical stress is reduced.

To compensate for wear of the second friction disc 5b, the second pressure plate 3b and / or the reaction plate 4, a second wear detection and correction means is mounted on the second clutch 2b.

The second wear detection and correction means mounted on the second clutch 2b is inserted between the second diaphragm 9b and the second pressure plate 3b in the axial direction.

The second wear detection and correction means includes a second moveable compensation member 13b present in the form of a ring which has an end capable of bearing bearing of the second diaphragm 9b, Comprises an end comprising at least one lamp 14b extending in the circumferential direction in cooperation with an associated counter-lamp 15b provided on the second pressure plate 3b.

The second wear detection and correction means also includes a second movable detection member 16b present in the form of a ring, the second movable detection member having an end at which the second diaphragm 9b can be bearing supported, And an end including at least one lamp 17b extending in the circumferential direction in cooperation with the counter-ramp 15b of the second pressure plate 3b.

For example, the angles of the lamps 14b, 17b of the movable members 13b, 16b and the counter-ramp 15b of the second pressure plate 3b are comprised between 2 and 20 degrees.

The two movable members 13b, 17b are concentric and separated from one another by, for example, a centering stud 34 (Fig. 13). In the embodiment shown in the drawings, the second movable detecting member 16b is located outside the corresponding second movable compensating member 13b in the radial direction. In a variant, the position of each of the movable members 13b, 16b can be reversed.

13 to 15, the detecting member 16b is a member which extends inward in the radial direction by crossing the notch 27b formed in the wear compensating member 13b in the radial direction, for example, Three legs 26b.

A first tension spring 18b extending in the circumferential direction is provided between the second detecting member 16b and the second pressure plate 3b.

More specifically, the spring 18b includes a hook shaped end 18'b that engages the integral rivet or stud of the second pressure plate 3b and a hooked end 18'b that engages the leg 26b of the detecting member 16b. quot; b " and is formed of wire.

Each end 18'b engages in a notch 26'b (Fig. 14) of the corresponding leg 26b.

For example, a second spring 19b such as a pin spring is provided between the second detecting member 16b and the second compensating member 13b.

The length of each first spring 18b is large enough to cause displacement of the second detecting member 16b in a large angular range (e.g., about 120 deg.).

The second clutch 2b also includes at least one second urging member 20b present in the form of an elastic tab that applies an axial load. The tab 20b is fixed to the pressure plate 3b in the first zone and is supported on the corresponding second end of the second detecting member 16b in the second zone and substantially on the second abrasion- Thereby restricting it to be supported on the second pressure plate 3b. Therefore, even if the second pressing member 20b is supported on the corresponding second end of the second detecting member 16b, even if the second pressing member 20b and the corresponding second There may be an axial gap between the ends.

The bearing stud 21b is fixed on the second section of the tab 20b. The bearing stud 21b is arranged in the radial direction between the second detecting member 16b and the second wear compensating member 13b and preferably radially between the movable members 13b and 16b, A first end 22b fixed by a rivet fastening and a cylindrical second end 23b defining an enlarged head of larger dimension than the rest of the stud 21b and defining a shoulder. The stud 21b may be supported on the radial face of the fixed lid 6 across the opening of the fixed lid 6. [

In particular, the enlarged head 23b of the bearing stud 21b is located at a position where the displacement of the second pressure plate 3b is large, i.e. when the lining of the second friction disk 5b and / It is designed to be bearing-supported on the reference surface 29f of the centering member 29 when the wear of the corresponding material of the pressure plate 3b is large.

Now, the operation of the second wear detection and correction means will be described with reference to Figs. 28 to 39. Fig.

As shown schematically in Figures 28-31, the second abrasion detection and correction means is used to determine if the lining of the second friction disk 5b is not at all or substantially abraded and the associated second pressure plate 3b and / If the corresponding material of the reaction plate 4 is not worn, for example, if the accumulated axial wear is less than 0.05 mm, it will not work.

28, the second diaphragm 9b is bearingly supported on the second compensating member 13b at the fully clutch engaged position and in the absence of wear, so that the second diaphragm 9b is biased against the second restoring member 13b against the resilient restoring tab 8b, Push the pressure plate (3b) again. The second pressure plate 3b and the corresponding reaction plate 4 (fixed in the axial direction) thus tighten the second friction disc 5b with the lining. In this position, the head 23b of the bearing stud 21b reaches the same level as the reference surface 29f of the centering member 29. [

Also in this position, the leg 26b is supported on the first edge 32b of the notch 27b of the compensating member 13b as shown in Fig.

30, the second diaphragm 9b is supported on the second detecting member 16b at the fully clutch disengaged position and there is no wear, and the second diaphragm 9b and the second diaphragm 9b are supported on the second detecting member 16b, A gap is generated between corresponding ends of the compensating member 13b.

The leg 26b is in a state of being supported on the first edge 32b of the notch 27b of the compensating member 13b as shown in Fig.

Thus, in the absence of significant wear, the second region of the elastic tab 20b and / or the second diaphragm 9b are configured such that whatever the actuation phase of the second clutch 2b (clutch engagement / disengagement of the clutch) It is confirmed that the detecting member 16b and the second compensating member 13b are supported and held on the second pressure plate 3b. In this case, the resistance torque generated by the friction between the members 13b, 16b and the second pressure plate 3b is larger than the torque applied by the springs 18b, 19b. Therefore, whatever the operation stage of the second clutch 2b is, the members 13b and 16b are immobilized on the rotation of the second pressure plate 3b.

32 to 39 show a state in which the lining of the second friction disc 5b (or the material of the second pressure plate 3b and the reaction plate 4) is greatly worn out to prevent malfunction of the second clutch 2b In the case where correction is required.

32, the head 23b of the bearing stud 21b is bearingly supported on the reference surface 29f of the centering member 29 at the fully clutch-connected position, so that the second The region falls from the corresponding second end of the second detecting member 16b. Therefore, a clearance j'1 is formed between the second end of the second detecting member 16b and the second end of the tab 20b.

In some cases, the end of the second detecting member 16b and the second end of the second detecting member 16b may be mixed. Likewise, the end of the second compensating member 13b and the second end of the second compensating member 13b can be mixed.

Accordingly, the second detecting member 16b, which is no longer subjected to the axial load, is rotationally interlocked by the first elastic member 18b to at least partially fill the gap j1 (Figs. 34 and 35). During this rotation, the second elastic member 19b is restricted. The direction of rotation of the detecting member 16b with respect to the compensating member 13b is shown by an arrow R'1 in Fig.

The rotation of the second detecting member 16b is stopped when the corresponding second end of the second detecting member 16b is again supported on the second section of the tab 20b, When the leg 26b is supported on the edge 33b (opposite the edge 32b) of the notch 27b of the compensating member 13b.

During this step, the second compensating member 13b is supported and held on the second pressure plate 3b by the second diaphragm 9b. Therefore, the member is immobilized in rotation with respect to the second pressure plate 3b.

During the subsequent clutch separating step, the second diaphragm 9b transfers its support from the second compensating member 13b to the second detecting member 16b. Figures 36-39 show the location of these elements during this migration. During this clutch disconnection, the second pressure plate 3b is released from the reaction plate 4 via the corresponding restoring tab 8b, releasing the second friction disc 5b.

As shown in Figs. 36 and 37, the second diaphragm 9b completely releases the second compensating member 13b at the fully clutch disengaged position. In this position, the second detecting member 16b is held on the second diaphragm 9b and on the second pressure plate 3b so that the rotation is held fixed. On the other hand, the head 23b of the bearing stud 21b is separated from the reference surface 29f of the centering member 29 and the second section of the movable tab 20b is moved relative to the corresponding second end of the second compensating member 13b (J'2).

Therefore, the second compensating member 13b, which is constrained by the second elastic member 19b, is rotationally interlocked as shown in Figs. 38 and 39 so that the second compensating member 13b between the second compensating member 13b and the tab 20b Thereby filling all or part of the gap j'2. The direction of rotation of the compensating member 13b with respect to the detecting member 16b is shown by an arrow R'2 in Fig.

The rotation of the second compensating member 13b may be achieved, for example, when the corresponding second end of the second compensating member 13b is again supported on the second section of the tab 20b, When the leg 26b is supported on the edge 32b of the notch 27b of the compensating member 13b, it is stopped.

The pivoting of the second compensating member 13b and the second detecting member 16b with respect to the second pressure plate 3b is carried out by means of the lamps 14b and 17b and the counter- 16b of the second diaphragm 9b and the second pressure plate 3b so that the wear of the lining of the second friction disk 5b and / or the wear of the second pressure plate 3b, The wear of the corresponding material of the plate 3b and the reaction plate 4 can be gradually compensated.

This structure also makes it possible to maintain the operating angle of the second diaphragm 9b, so that a constant preload load is maintained and the mechanical stress is reduced.

In each of the embodiments disclosed above, the restoring means of the pressure plates 3a, 3b (formed by the elastic tabs 8a, 8b) can exert a large load, which is applied to the corresponding movable compensating member 9b by the corresponding diaphragms 9a and 9b or the corresponding movable detecting members 16a and 16b and then to the corresponding diaphragms 9a and 9b according to the positions of the diaphragms 9a and 9b . In fact, since the movable members 13a, 13b, 16a and 16b are not subjected to the loads applied by the restoring means 8a and 8b of the pressure plates 3a and 3b during their displacement, the springs 18a and 18b , 19a, 19b). ≪ / RTI >

Since the restoration means 8a and 8b of the pressure plates 3a and 3b exhibiting a large load are disposed, for example, as the spring taps 8a and 8b having high rigidity, the transmission of the axial vibration can be restricted The pumping phenomenon can be prevented.

Further, since the tabs 20a and 20b forming the pressing member are fixed to the fixed lid 6 and the pressure plate 3b, respectively, they are not subjected to the fatigue phenomenon due to the clutch connecting and clutch disengaging cycles in operation.

The first wear detection and correction means is positioned between the first diaphragm 9a and the fixed lid 6 and the second wear detection and correction means is positioned between the second diaphragm 9b and the second pressure plate 3b, It is possible to simplify the structure of the dual clutch 1 and to reduce its radial charge volume and by arranging the wear detection and correction means between the members which undergo less deformation during operation, Thereby allowing better control of the operation of the means. Thus, the position of the movable members 13a, 13b, 16a, 16b is better controlled.

On the other hand, since each of the bearing studs 21a, 21b is connected to the second end of the corresponding tab 20a, 20b, the deformation of the second end can be reduced to the greatest extent so that different movable elements 13a, 13b , 16a, 16b can be best controlled, and therefore the correction of wear can be best controlled.

Finally, the centering member 29, at the same time,

The centering of the detecting member 16a,

The centering of the abrasion-compensating member 13a,

The support of the bearing stud 21b,

A radial guide of the elastic member 18a,

- engagement of the end 18'a of the elastic member 18a,

The centering of the first diaphragm 9a,

- Installation of the centering stud of the second diaphragm (9b)

.

Thus, the cost and complexity of the dual clutch can be reduced, since only one member ensures multiple functions.

The present invention is also applicable to a normally closed type clutch.

Claims (10)

At least one reaction plate 4 designed to be rotationally coupled to the drive shaft about a rotational axis X,
First and second friction disks (5a, 5b), each having a friction lining, designed to be coupled to the first and second driven shafts, respectively,
The first and second diaphragms (9a, 9b) respectively actuated by the first and second diaphragms (9a, 9b) in such a manner as to tighten or loosen the first and second friction discs (5a, The first pressure plate 3a is fixedly connected to the lid 7 which translationally moves with respect to the reaction plate 4 and the first pressure plate 3a is fixedly connected to the first lid 7, The first and second pressure plates (3a, 3b), which are actuated by supporting the diaphragm (9a)
A fixed lid 6 fixed to the reaction plate 4 and receiving a second pressure plate 3b, a second friction disk 5b and / or a second diaphragm 9b,
A wear-compensating dual clutch (1), particularly for an automobile, comprising first wear detection and correction means capable of correcting wear of a first friction disk (5a)
Wherein the first wear detection and correction means comprises:
A first abrasion correction means (13a) inserted between a first diaphragm (9a) and a fixed lid (6), comprising at least one compensating member (13a) moving in a predetermined range and being provided on the fixed lid (15a) to adjust the distance between the first diaphragm (9a) and the stationary lid (6) and to adjust the distance to the counter-ramp (15a) (13a), (13a), (13b), and (13b)
The first wear detection means 16a capable of displacing the movable compensation member 13a in the case of abrasion and interfering with such displacement when such abrasion is insufficient, The first wear detection means 16a including a lamp 17a cooperating with a counter-ramp 15a which includes one movable detection member 16a and which is located on the side of the fixed lid 6, and
At least one first urging member (20a) for restricting at least the ramp (17a) of the detecting member (16a) relative to the associated counter-ramp (15a) , Said at least one first urging member (20a) being capable of cooperating with a stationary stopper (21a)
The movable compensating member 13a is driven to be displaced when the movable compensating member 13a is released by the first diaphragm 9a,
The movable detecting member 16a is displaced when the movable detecting member 16a is released by the pressing member 20a and by the first diaphragm 9a and is displaced by itself and the first pressing member (1), which is driven by an elastic member (18a) to at least partly correct a gap (j1, j'1)
The detecting member 16a is provided with at least one leg which can be supported on the corresponding at least one bearing of the movable compensating member 13a so that the displacement of the detecting member 16a relative to the movable compensating member 13a is limited, Characterized in that the elastic member (18a) for driving the detecting member (16a) is fixed or hooked to the leg (26a) of the detecting member (16a) at one end
Wear compensation dual clutch. The method according to claim 1,
And second wear detection and correction means capable of correcting wear of the second friction disk, wherein the second wear detection and correction means comprises:
A second wear compensating means 13b inserted between the second diaphragm 9b and the second pressure plate 3b and including at least one compensating member 13b moving in a predetermined range, And a lamp 14b cooperating with the counter-ramp 15b located on the side of the counter-ramp 15b to adjust the distance between the second diaphragm 9b and the second pressure plate 3b, The second abrasion correction means 13b, which compensates for the corresponding abrasion according to the position of the lamp 14b relative to the second abrasion correction means 13b,
And a second wear detection means (16b) capable of displacing the movable compensation member (13b) in the case of abrasion and interfering with such displacement when such abrasion is insufficient, characterized in that the movable compensation member The second abrasion detection means 16b, which comprises a lamp 17b which cooperates with a counter-ramp 15b which comprises at least one movable detection member 16b and which is located on the side of the second pressure plate 3b,
At least one second urging member (20b) for restricting at least the ramp (17b) of the detecting member (16b) relative to the associated counter-ramp (15b), wherein when the abrasion is detected, the corresponding detecting member (20b) capable of cooperating with the stationary stopper (21b) in such a manner that the first stop member
The movable compensating member 13b is driven to be displaced when the movable compensating member 13b is released by the second diaphragm 9b,
The movable detecting member 16b is displaced and fixed between itself and the pressing member 20b when the movable detecting member 16b is released by the second pressing member 20b and by the second diaphragm 9b Lt; RTI ID = 0.0 > (j1, j'1) < / RTI &
The detecting member 16b is provided with at least one leg 26b which can be supported on a corresponding at least one bearing of the compensating member 13b so that the displacement of the detecting member 16b relative to the movable compensating member 13b is limited, , And an elastic member (18b) for driving the detecting member (16b) is fixed or hooked to the leg (26b) of the detecting member (16b) at one end
Wear compensation dual clutch. 3. The method according to claim 1 or 2,
The legs 26a and 26b of the detecting members 16a and 16b of the first or second abrasion detecting and correcting means cross the notches 27a and 27b of the corresponding movable compensating members 13a and 13b, (26a, 26b) can be bearing supported against the edges of the notches (27a, 27b)
Wear compensation dual clutch. The method of claim 3,
Characterized in that the notches (27a, 27b) are open on the side of the fixed lid (6) or the second pressure plate (3b)
Wear compensation dual clutch. 5. The method according to any one of claims 1 to 4,
The detecting members 16a and 16b can pivot about the movable correction members 13a and 13b about the axis and the legs 26a and 26b of the detecting members 16a and 16b are movable relative to the movable correction members 13a and 13b ) Of the detecting members (16a, 16b) to an angle of less than 5 degrees
Wear compensation dual clutch. 6. The method according to any one of claims 1 to 5,
The elastic members 18a and 18b for driving the detecting members 16a and 16b of the first or second abrasion detecting and correcting means are formed by notches of the legs 26a and 26b of the corresponding detecting members 16a and 16b Characterized in that it comprises an end formed by a wire in the form of a hook which engages in a groove
Wear compensation dual clutch. 7. The method according to any one of claims 1 to 6,
The movable compensating members 13a and 13b and the detecting members 16a and 16b of the first or second abrasion detecting and correcting means each include an annular portion including corresponding lamps 14a and 14b and 17a and 17b, The annular portion of the detecting members 16a and 16b is positioned radially outward of the annular portion of the compensating members 13a and 13b and the legs 26a and 26b of the detecting members 16a and 16b are located on the opposite sides of the detecting members 16a and 16b And the free ends of the legs 26a and 26b are located radially inward of the annular portion of the compensating members 13a and 13b and the corresponding detecting members 16a and 16b are located radially inward of the annular portion of the compensating members 13a and 13b, Characterized in that the elastic members (18a, 18b) for driving the legs (26a, 26b) are fixed to the free ends of the legs (26a, 26b)
Wear compensation dual clutch. 8. The method according to any one of claims 1 to 7,
And a centering member (29) fixed to the fixed lid (6), wherein the centering member (29) includes a cylindrical guide surface (29i) or is partially cylindrical, and the detecting member The centering member 16a is annular and includes three or more legs 26a extended in the radial direction to be supported on the centering surface 29i of the centering member 29 to ensure centering of the detecting member 16a doing
Wear compensation dual clutch. 9. The method according to any one of claims 1 to 8,
The legs 26a and 26b are inserted between the counterbrains 15a and 15b of the fixed lid 6 or the second pressure plate 3b and the movable compensating members 13a and 13b in the axial direction
Wear compensation dual clutch. 10. The method according to any one of claims 3 to 9,
The notches 27a and 27b are arranged at an angle between two consecutive lamps 14a and 14b of the movable compensating members 13a and 13b
Wear compensation dual clutch.

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